EP0118573B1 - Leistungsfähigkeitssteuervorrichtung für einen mengenregelbaren Verdichter in einer Klimaanlage - Google Patents

Leistungsfähigkeitssteuervorrichtung für einen mengenregelbaren Verdichter in einer Klimaanlage Download PDF

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Publication number
EP0118573B1
EP0118573B1 EP83102268A EP83102268A EP0118573B1 EP 0118573 B1 EP0118573 B1 EP 0118573B1 EP 83102268 A EP83102268 A EP 83102268A EP 83102268 A EP83102268 A EP 83102268A EP 0118573 B1 EP0118573 B1 EP 0118573B1
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EP
European Patent Office
Prior art keywords
compressor
temperature
signal
vsv
air conditioning
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Expired
Application number
EP83102268A
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English (en)
French (fr)
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EP0118573A1 (de
Inventor
Tamura Yasuji
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Sanden Corp
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Sanden Corp
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Publication date
Priority to AU12018/83A priority Critical patent/AU561404B2/en
Application filed by Sanden Corp filed Critical Sanden Corp
Priority to EP83102268A priority patent/EP0118573B1/de
Priority to DE8383102268T priority patent/DE3375842D1/de
Publication of EP0118573A1 publication Critical patent/EP0118573A1/de
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Publication of EP0118573B1 publication Critical patent/EP0118573B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D23/00—Control of temperature
    • G05D23/19—Control of temperature characterised by the use of electric means
    • G05D23/1906—Control of temperature characterised by the use of electric means using an analogue comparing device
    • G05D23/1912—Control of temperature characterised by the use of electric means using an analogue comparing device whose output amplitude can take more than two discrete values
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D23/00—Control of temperature
    • G05D23/19—Control of temperature characterised by the use of electric means
    • G05D23/20—Control of temperature characterised by the use of electric means with sensing elements having variation of electric or magnetic properties with change of temperature
    • G05D23/24—Control of temperature characterised by the use of electric means with sensing elements having variation of electric or magnetic properties with change of temperature the sensing element having a resistance varying with temperature, e.g. a thermistor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/327—Cooling devices output of a control signal related to a compressing unit
    • B60H2001/3275—Cooling devices output of a control signal related to a compressing unit to control the volume of a compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation

Definitions

  • This invention relates generally to a device for controlling the operation of an air conditioning system, and more particularly, to an electronic capacity control circuit for a variable displacement compressor in an automobile air conditioning system according to the preamble of Claim 1.
  • the air conditioning compressor is driven by a motor, either directly or through a magnetic clutch.
  • Thermal control in the room or compartment is accomplished by the intermittent operation of the magnetic clutch or motor by a signal from a thermostat disposed in the room.
  • the supplemental cooling capacity of the air conditioner need not be as large for maintaining the desired temperature in the room. Therefore, after the room has been cooled to the desired temperature, conventional air conditioning compressors are intermittently operated in response to the thermostat signal. Compressors having large cooling capacities are operated even more intermittently because of the high amounts of energy required to drive such compressors.
  • the compressor In an air conditioning system for automobiles, the compressor is usually driven by the automobile engine. Because the r.p.m. of the automobile engine changes continuously, the rotation frequency of the compressor changes accordingly, resulting in rapid changes in the cooling capacity of the air conditioner.
  • Automobile air conditioners are generally designed so that when the compressor is driven by the engine at normal driving speeds, the air conditioner operates at optimum capacity. Therefore, when the compressor is driven by the engine at lower operating speeds, or when the engine is idling, the cooling capacity of the air conditioner is insufficient to maintain adequate cooling of the vehicle. Conversely, when the compressor is driven at high operating speeds by the engine, cooling capacity is more than necessary.
  • One known device for controlling the excessive cooling capacity of air conditioning systems operates by reheating some of the cooled air generated by the air conditioner. Part of the air from the evaporator of the air conditioner is reheated in a heating unit. The reheated air is mixed with the remaining cooled air to control the temperature of the air which is ultimately blown into the room or compartment. In this device, the ratio of cooling capacity to heating capacity is controlled in response to the r.p.m. of the automobile engine.
  • the above described device for controlling air temperature is complicated and considerable energy is wasted in reheating the cooled air.
  • the magnetic clutch connecting the compressor to the driving engine or motor is intermittently operated to control the operation of the compressor.
  • the magnetic clutch is often required to engage the driving engine at high operating speeds, sudden and deleterious forces are generated at the moment the clutch is engaged and are transmitted to the engine and compressor.
  • the temperature of the air which is blown into the room or compartment also drastically changes upon engagement of the clutch and operation of the compressor.
  • a capacity control device for a compressor in an air conditioning system comprises a variable displacement device for changing the capacity of the compressor by a servo motor which can be driven in both directions and a control circuit, which includes a temperature detector and comparators, which compare a signal from the temperature detector with threshold values corresponding to desired temperatures in order to generate a control signal for the variable displacement device.
  • GB-A-2 039 386 The utilization of a microprocessor in an automatic control arrangement for controlling a variable capacity compressor for air conditioning systems is known from GB-A-2 039 386 and two signals for a count pulse and up/down mode selection are produced from a sensed signal provided by a temperature sensor.
  • a control system for environmental conditional units which comprises a control device including control units for generating a control signal as well as actuating means for actuating one of a plurality of environmental units in response to the control signal.
  • the control means comprises a temperature detecting means and an up/down counting means for selectively carrying out count up operation and count down operation.
  • the counting means are connected to the actuating means.
  • DE-A1-3 133 502 discloses the use of solenoid-operated valves in an air conditioning system.
  • a specific object of this invention is to provide a control circuit for the cooling capacity of the air conditioning compressor as required by the cooling load which eliminates or reduces the generation of sudden and deleterious forces when the compressor engages the driving device and which improves the performance and efficiency of the air conditioning system.
  • the present invention is directed to a device for controlling the cooling capacity of a compressor in an air conditioning system which is characterized by the features of the characterizing portion of claim 1.
  • the air conditioning system comprises a compressor as generally indicated by reference number 1.
  • Compressor 1 includes magnetic clutch 8 and variable displacement device 9 which are controlled by control circuit 10 as will be explained in greater detail below.
  • the air conditioning system shown in Figure 1 further comprises condensor 2 and its associated fan 6, receiver and dryer 3, thermostatic expansion device or valve 4 and evaporator 5 and its associated fan 7. These basic components are coupled in series to form a conventional refrigeration circuit. Refrigerant gas is compressed in compressor 1 and supplied to condensor 2 where it is condensed to liquid refrigerant and cooled by forced ventilation of fan 6.
  • the liquid refrigerant is accumulated in receiver and dryer 3, which removes the moisture and metal chips from the liquid refrigerant.
  • the liquid refrigerant within the receiver and dryer 3 is delivered to thermostatic expansion valve 4.
  • the refrigerant expands as it flows through valve 4 and emerges as a two-part mixture of liquid and gas, but primarily liquid.
  • evaporator 5 acts as a heat exchanger in conjunction with blower 7, which supplies air to the vehicle compartment, heat is transferred from the incoming air to the refrigerant and the entirety of the refrigerant vaporizes to a gaseous state.
  • the refrigerant gas at the evaporator outlet is then passed to the suction inlet of compressor 1.
  • Compressor 1 is controlled by the operation of magnetic clutch 8 and variable displacement device 9.
  • Magnetic clutch 8 is used to engage the compressor driving means and variable displacement device 9 is used for changing the cooling capacity of the compressor, both being controlled by the operation of control circuit 10 as will be described in further detail below.
  • Variable displacement device 9 may be used to change the cooling capacity of compressor 1 to one of three levels, i.e., CC,, CC 2 or CC 3 , as shown in Figure 2.
  • Figure 2 illustrates the relationship of cooling capacity to rotation frequency of the compressor.
  • compressor 1 is a scroll type compressor including a variable displacement device 9.
  • Compressor 1 is controlled by operation of magnetic clutch 8 which controls the operation thereof and the variable displacement device 9 which changes the cooling capacity of the compressor.
  • Magnetic clutch 8 and variable displacement device 9 are controlled by operation of control circuit 10, which is described in further detail below in connection with Figure 3.
  • compressor 1 includes variable displacement device 9 which is capable of changing the cooling capacity of the compressor.
  • the capacity of the compressor shown in Figure 1 can be changed to one of three conditions, i.e., CC,, CC 2 or CC 3 , as shown in Figure 2.
  • Variable displacement device 9 of compressor 1 includes at least one valve. This valve is controlled by a solenoid.
  • variable displacement device 9 of compressor 1 has two valves and two solenoids VSV, and VSV 2 as shown in Figure 3. Solenoids VSV, and VSV 2 are connected to voltage source Vcc through control circuit 10.
  • control circuit 10 for controlling the operation of magnetic clutch 8 and variable displacement device 9 of compressor 1 is shown.
  • the control circuit includes a temperature detecting circuit A which detects the temperature of blown airfrom evaporator 5. The detected temperature is compared with predetermined temperature levels to generate signals for controlling magnetic clutch 8 and variable displacement device 9 through the operation of solenoids VSV, and VSV 2 as shown in circuit B.
  • Temperature detecting circuit A includes temperature sensing thermistor Th and comparators OP 1 , OP 2 and OP 3 .
  • Thermistor Th is mounted on the air outlet of evaporator 5 for detecting the temperature of the blown air.
  • reference voltages V 3 and V 1 are set by variable resistor VR through voltage divider network R 2 , R 3 and R 4 in accordance with predetermined temperatures Tu and Td. That is, the predetermined temperatures Tu and Td are set by adjusting the resistance of variable resistor V R .
  • Reference voltages V 3 and V 1 establish the upper temperature (Tu) and lower temperature (Td) levels of the air blown from evaporator 5 at which the outputs of comparators OP 3 and OP 1 change voltage levels, respectively.
  • the outputs of comparators OP 1 and OP 3 are coupled to clock terminal C of up/down counter 11 via respective coupling networks.
  • the coupling network of OP 1 includes resistors R s and R s , diodes D 1 and D 3 and capacitor C 1 .
  • the coupling network of OP 3 similarly includes resistors R 7 and R 4 , diodes D 2 and D 4 and capacitor C 2 .
  • Capacitors C 1 and C 2 of each respective coupling network convert the high voltage output signals of comparators OP 1 and OP 3 to a pulse signal which is used to drive clock terminal C of counter 11.
  • Output voltage V 5 of comparator OP 2 is coupled to the up/down terminal input of counter 11 and determines whether counter 11 counts in an upward or a downward direction in response to the pulse signals from capacitors C 1 and C 2 .
  • Resistor R 6 at the output of comparator OP 2 provides the proper biasing for the up/down terminal of counter 11.
  • the output of counter 11 is provided at output terminals O 1 and 0 2 in binary format.
  • reference voltage V 2 of comparator OP 2 is set between reference voltages V 1 of comparator OP 1 and reference voltage V 3 of comparator OP 3 . Therefore, when the output of comparator OP 1 is at a high voltage level, the output of comparator OP 2 is also at a high voltage level. Accordingly, the pulse signal generated by the changing of the output voltage level of comparator OP 1 is counted in the upward direction by counter 11 while the pulse signal generated by the changing of the output voltage level of comparator OP 3 is counted in the downward direction since the voltage level of the up/down terminal of counter 11 is then at a low state.
  • Control circuit 10 further includes logic circuit B for controlling the operation of magnetic clutch 8 and solenoids VSV, and VSV 2 in accordance with the outputs of counter 11.
  • the operation of magnetic clutch 8 is controlled by the operation of relay Ry.
  • Relay Ry is connected to the collector of NPN type transistor Tr 1 which is in turn connected in series with magnetic clutch 8. When transistor Tr 1 conducts, relay Ry is energized so that magnetic clutch 8 actuates compressor 1.
  • the base of transistor Tr 1 is connected to counter 11 via a logic circuit including OR gate G 7 , AND gate G 6 and converters G 1 and G 2 .
  • Resistor R 18 is connected between the base of transistor Tr 1 and OR gate G 7 to provide proper biasing.
  • solenoids VSV, and VSV 2 The operation of solenoids VSV, and VSV 2 is controlled by NPN type transistors Tr 2 and Tr 3 .
  • the collector of each transistor is connected in series with solenoids VSV, and VSV 2 , respectively.
  • solenoids VSV, and VSV 2 actuate valves in variable displacement device 9 for changing the displacement of compressor 1.
  • the base of transistor Tr 2 is coupled to counter 11 via AND gate G 8 and inverter G 3 .
  • the base of transistor Tr 3 is coupled to counter 11 via OR gate G 11 , AND gates G 9 and G 10 and inverters G 4 and G s .
  • Resistors R 19 and R 20 provide proper biasing for transistors Tr 2 and Tr 3 , respectively.
  • magnetic clutch 8 and solenoids VSV, and VSV 2 is in accordance with the outputs O 1 and O 2 of counter 11 as shown below in Table II where "0" represents a low level voltage output and "1" represents a high level voltage output.
  • a pulse signal at terminal C of counter 11 is generated by the output of comparator OP 1 when temperature Te of the blown air at evaporator 5, as detected by thermistor Th, decreases from a high level to predetermined lower temperature level Td.
  • This pulse signal changes the count of counter 11 which ultimately reduces the capacity of the compressor by operation of circuit B.
  • a pulse signal is generated at terminal C of counter 11 by the output of comparator OP 3 when temperature Te increases to upper predetermined temperature level Tu in response to the reduction in compressor capacity described above.
  • the cooling capacity of compressor 1 can be continuously controlled by these two pulse signals.
  • Control circuit 10 also includes auxiliary circuit C which is responsive to the pulse signal generated by the outputs of comparators OP 1 and OP 3 through inverter G 13 .
  • auxiliary circuit C includes RS flip-flop 12 with outputs Q and Q connected to comparators OP 4 and OP S via respective coupling networks R 10 and C 3 and D 5 , R 14 and C 4 .
  • Resistors R 11 , R 12 and R 13 establish reference voltage V 7 for comparator OP 4 and the voltage V 7 is compared with the output voltage V 8 of output Q of flipflop 12.
  • resistors R 15 and R 16 establish reference voltage V 9 for comparator OP S and the voltage Vg is compared with the output voltage V, o of output Q of flip-flop 12.
  • the output of comparator OP 5 is coupled via capacitor C 5 and resistor R 17 to the reset terminal of flip-flop 12 through inverter G 12 .
  • the output of comparator OP 4 is coupled to the cathodes of diodes D, and D 2 of circuit A.
  • auxiliary circuit C When the air conditioner is first started, temperature Te of the blown air in evaporator 5 is high so that voltage V T , which is inversely related to temperature Te, is lower than reference voltage V 3 applied to the non-inverting input terminal (+) of comparator OP 3 .
  • the output of comparator OP 3 is at a high voltage level and the outputs of comparators OP 1 and OP 2 are at a low voltage level.
  • compressor 1 is driven with large cooling capacity or volume CC 1 as shown in Figure 2 so that the desired room temperature is quickly reached.
  • voltage V T then increases in accordance with the lowering of temperature Te of the blown air as shown in Figure 4.
  • the pulse signal which is generated by capacitor C 1 is inverted by inverter G 13 , as shown by waveform V s in Figure 4, and is input to set terminal S of flip-flop circuit 12.
  • the voltage at point a of the output line of comparator OP 1 is held to a low voltage level for a predetermined time delay T 1 , e.g., five seconds.
  • Delay T 1 is established by comparator OP 4 and a timer circuit which includes comparator OP 5 .
  • flip-flop 12 Prior to pulse V S being applied to terminal S of flip-flop 12, flip-flop 12 is in a reset condition with output terminal Q held to a high voltage level and output terminal Q held to a low voltage level.
  • output voltage V 11 of comparator OP 4 is at a high level and the output voltage of comparator OP 5 is at a low level.
  • pulse signal V s is applied to terminal S of flip-flop 12, the voltage levels of outputs Q and Q change to high and low, respectively.
  • time delay Th 1 which is established by a time constant circuit comprising capacitor C 3 and resistor R 10 , output voltage V 11 of comparator OP 4 changes to a low level. That is, as shown in Fig. 4, voltage V 8 is gradually reduced due to discharge of capacitor C 3 and, when voltage V 8 is below the reference voltage V 7 , output voltage V 11 of comparator OP 4 changes to a low level.
  • the presence of time delay TH 1 prevents the changing of output voltage V 11 of comparator OP 4 from interfering with the pulse signal present at point a of the output line of comparator OP 1 when its output changes from a low to a high voltage level.
  • the output voltage of comparator OP S changes to a high level and a reset signal is generated by capacitor C 5 , shown as VR in Figure 4, and is provided to reset the terminal R of flip-flop circuit 12 via inverter G 12 . Accordingly, flip-flop 12 is reset to the state where output terminal Q is at a low voltage level and output terminal Q is at a high voltage level.
  • Output voltage V " of comparator OP 4 also changes to a high voltage level after time delay T RS which is established by the time constant circuit. That is, the voltage V 8 is gradually increased due to charge of capacitor C 3 and, when the voltage V 8 exceeds the reference voltage V 7 , the output voltage V 11 changes to a high voltage level.
  • variable displacement device 9 operates continuously to maintain the temperature around lower temperature Td.
  • the continuous operation around higher temperature Tu can also be accomplished in a similar manner.
  • control circuit 10 will now be decribed with reference to the flow diagram shown in Figure 5.
  • Step 12 determines the compression volume of compressor 1, such as large volume CC,, to which the air conditioning system will be initially set.
  • step 13 is a subroutine for controlling solenoids VSV, and VSV 2 for actually setting the compression volume, as shown in Figure 6.
  • control circuit 10 After setting lower and higher temperature T, and T 2 , respectively, the operation of control circuit 10 proceeds to step 15. At step 15, temperature Te of the air blown into the compartment is detected and compared with lower predetermined temperature Td from detecting circuit A of control circuit 10. If temperature Te is higher than lower predetermined temperature Td, operation of control circuit 10 proceeds to step 16 which determines the current volume of compressor 1. If the volume of compressor 1 is set to large volume CC, the operation of control circuit 10 proceeds to step 17 and compressor 1 continues to be driven with large volume CC,. While Te remains higher than temperature Td, the operation of control circuit 10 continuously flows back through closed loop steps 15, 16, 17 and back to 15 to continue the operation of compressor 1 with. large volume CC,.
  • step 23 the compression volume of compressor 1 is compared with the smallest volume CC 3 of compressor 1 and if the present volume of compressor 1 is larger than volume CC 3 , step 23 flows to step 25 which operates to reduce the volume of compressor 1 through the operation of solenoids VSV, and VSV 2 of variable displacement device 9 by logic circuit B of control circuit 10.
  • step 24 flows to step 25 which is the same subroutine as shown in Figure 6.
  • step 25 flows to step 26 which operates the setting of the time delay used by circuit C of control circuit 10.
  • step 27 temperature Te of the blown air is detected and compared with higher predetermined temperature Tu. If temperature Te is lower than the predetermined temperature Tu, step 27 proceeds to steps 33 and 34. The operation of control circuit 10 then continuously flows back through closed loop steps 35, 27, 33 and 34 until the end of predetermined time delay t which is set in step 26. After time delay t, if temperature Te of the blown air has increased higher than predetermined temperature Tu, step 27 proceeds to step 28, 29, 30, 31 and 32. In step 32, the compression volume of compressor 1 is returned to large volume CC 1 from middle volume CC 2 because the refrigerating capacity of compressor 1 with middle volume CC 2 is insufficient for the refrigeration load.
  • step 35 proceeds to step 36.
  • Step 36 compares the temperature Te of the blown air with the lower predetermined temperature Td. If temperature Te of the blown air is lower than predetermined temperature Td, step 36 proceeds to steps 37, 23 and 24 where the compression volume is reduced. If, however, temperature Te of the blown air is higher than lower predetermined temperature Td, step 36 flows back to step 27 and the compressor is driven with the present compression volume. In this situation, temperature Te of the blown air is maintained within a range between temperature T, (Td) and T 2 (Tu).
  • Compressor 1 is driven with smaller volume CC 3 at step 25, and predetermined time delay t is set at step 26.
  • time delay t the operation of control circuit 1 flows through closed loop steps 27, 33, 34, 35 and 27 to detect the change in temperature of the blown air, Te.
  • Te increases above predetermined temperature Td, this indicates that the refrigerating capacity is insufficient for the refrigeration load, and the operation of control circuit 1 flows to step 28, 29, 30 and 31, where smaller compression volume CC 3 is returned to middle volume CC 2 and then the operation proceeds to step 15.
  • step 37 proceeds to steps 23 and 39.
  • step 39 the compressor is stopped by the operation of magnetic clutch 9 using logic circuit B in control circuit 10. However, if temperature Te of the blown air is higher than lower predetermined temperature Td, the operation of the compressor 1 is continued with smaller volume CC 3 due to the return to step 27.
  • step 37 temporarily replaces lower predetermined temperature Td.
  • the changing of compression volume is started at the moment that the temperature Te of the blown air reaches lower predetermined temperature Td.
  • Td-a which is lower than first determined temperature Td. Therefore, the refrigerating capacity of smaller volume CC 3 of compressor 1 must be compared with temperature Td-a. If, in step 36, the control circuit detects that the refrigerating capacity of compressor 1 is higher, step 36 proceeds to step 37 to determine another lower predetermined temperature T1. However, this temporary lower predetermined temperature will be set back to its primary temperature at step 28.
  • control circuit 10 particularly, its operation after step 18 will be described with reference to Figures 5 and 7.
  • step 18 when the compressor is driven with middle volume CC 2 or smaller volume CC 3 , the refrigerating capacity of compressor 1 is insufficient at point P by changing of operating conditions, for example, driving speed of compressor is reduced, the temperature of the blown air is increased as shown by the dotted line in Figure 7.
  • step 18 proceeds to step 19 which sets the timer mechanism to determine the predetermined time C to prevent the unnecessary changing of compression volume in order to prevent the blowing of warm air.
  • step 19 proceeds back to step 15 and to closed loop steps 15, 16, 18, 19, and 15. Since the operation flow after point 18 operates to increase the compression volume in the step 16, the compression volume of compressor 1 is detected. In step 16, if compressor 1 is driven with large volume CC,, the operation flow after step 18 is prevented.
  • step 19 then proceeds to step 20 which compares temperature Te of the blown air with higher predetermined temperature Tu.
  • step 20 if temperature Te of the blown air is higher than higher predetermined temperature Tu, the refrigerating capacity of compressor 1 is insufficient for the refrigeration load and step 20 proceeds to steps 21,30 and 31 where the refrigerating capacity of compressor 1 is increased at step 31.
  • step 21 has the same function as the step 27 and temporarily determined temperature T 2 is set back to its primary predetermined temperature, at step 22.
  • control circuit 10 establishes three different temperatures; Tu, Tm and TL which are used to control the operation of magnetic clutch 8 and variable displacement device 9.
  • Tu is the starting point of operation of magnetic clutch 8 and is also the point where compression volume is changed to a larger volume from a smaller volume.
  • Tm is the changing point of the compression volume to a smaller volume from a larger volume
  • lower predetermined temperature TL is the stopping point of the operation of magnetic clutch 8 and also the changing point of compression volume to a smaller volume from a larger volume.
  • temperature Te of blown air is decreased by the operation of the compressor, which has a large volume CC, and reaches middle predetermined temperature Tm (this state is shown at point P in Figure 8).
  • the compression volume of the compressor then changes to middle volume CC 2 from large volume CC,. If the refrigerating capacity of compressor 1 is insufficient in comparison to the refrigeration load, temperature Te increases, as shown by the dotted line in Figure 8. Therefore, the temperature Te keeps within the range of determined temperature Tu and Tm in order to change the volume of compressor 1 between large volume CC, and middle volume CC 2 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (2)

1. Steuereinrichtung (10) für eine Klimaanlage mit einer Steuereinheit (A, B, C) zum Ändern der Kühlkapazität der Klimaanlage, wobei die Steuereinheit (A, B, C) eine Auswerteeinheit (A) mit einer Temperaturerfassungseinrichtüng (Th) zum Erzeugen eines Temperatursignales (VT), eine erste Vergleichseinrichtung (OP2) zum Vergleichen des Temperatursignales (VT) mit einer ersten Vergleichsspannung (V2), die mit einem ersten vorbestimmten Temperaturpegel in Beziehung steht, und Erzeugen eines ersten Signales (V5), und einer auf das erste Signal (V5) reagierende Vorwärts-Rückwärts-Zähleinrichtung (11) zum binären Vorwärts- und Rückwärtszählen, wenn das erste Signal (V5) sich in einem ersten Zustand bzw. in einem zweiten Zustand befindet, und Vorsehen eines Steuersignales (O1, O2) und eine auf das Steuersignal (O1, 02) reagierende logische Schalteinrichtung (B) zum Erzeugen einer Mehrzahl von Freigabesignalen zum Ändern der Kühlkapazität der Klimaanlage aufweist, dadurch gekennzeichnet
―daß die Klimaanlage einen Kompressor (1) mit einer variablen Verdrängungsvorrichtung (9) aufweist,
- daß die Auswerteeinheit (A) eine zweite Vergleichseinrichtung (OP,), die das Temperatursignal (VT) mit einer zweiten Vergleichsspannung (V1), die mit einem zweiten vorbestimmten Temperaturpegel (Tu) in Beziehung steht, vergleicht und ein zweites Signal vorsieht, und eine dritte Vergleichseinrichtung (OP3), die das Temperatursignal (VT) mit einer dritten Vergleichsspannung (V3), die mit einem dritten vorbestimmten Temperaturpegel (Td) in Beziehung steht, vergleicht und ein drittes Signal vorsieht, wobei das zweite und dritte Signal dem Takteingang der Zähleinrichtung (11) zugeführt werden, aufweist,
―daß eine mit der Zähleinrichtung (11) und der zweiten und dritten Vergleichseinrichtung (OP1, OP3) gekoppelte Zeitgebereinrichtung (C) vorgesehen ist zum Erzeugen eines vierten Signales (V11) eine vorbestimmte Zeit (Th1) nach Erzeugung des zweiten bzw. dritten Signales,
―daß die Zähleinrichtung (11) das zweite und dritte Signal als Reaktion auf das erste Signal (V5) zählt,
- daß die logische Schalteinrichtung (B) die Freigabesignale zum Freigeben einer Betätigungseinrichtung (VSV1, VSV2) zum Erregen der variablen Verdrängungsvorrichtung (9) in dem Kompressor (1) zum Ändern der Kapazität des Kompressors (1) erzeugt.
2. Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Betätigungseinrichtung (VSV1, VSV2) ein erstes Ventil (VSV,) und ein zweites Ventil (VSV2) aufweist, wobei die logische Schalteinrichtung (B) auf das Steuersignal (O1, 02) der Binärzählung reagierend gebildet ist zum Erzeugen der Mehrzahl von Freigabesignalen zum Freigeben des ersten und zweiten Ventiles (VSV1, VSV2) zum Ändern der Kapazität des Kompressors (1).
EP83102268A 1983-03-08 1983-03-08 Leistungsfähigkeitssteuervorrichtung für einen mengenregelbaren Verdichter in einer Klimaanlage Expired EP0118573B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU12018/83A AU561404B2 (en) 1983-03-08 1983-03-03 Variable capacity compressor
EP83102268A EP0118573B1 (de) 1983-03-08 1983-03-08 Leistungsfähigkeitssteuervorrichtung für einen mengenregelbaren Verdichter in einer Klimaanlage
DE8383102268T DE3375842D1 (en) 1983-03-08 1983-03-08 A capacity control device for controlling a variable displacement compressor in an air conditioning system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP83102268A EP0118573B1 (de) 1983-03-08 1983-03-08 Leistungsfähigkeitssteuervorrichtung für einen mengenregelbaren Verdichter in einer Klimaanlage

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EP0118573A1 EP0118573A1 (de) 1984-09-19
EP0118573B1 true EP0118573B1 (de) 1988-03-02

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EP (1) EP0118573B1 (de)
AU (1) AU561404B2 (de)
DE (1) DE3375842D1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006072838A1 (en) * 2005-01-03 2006-07-13 Arcelik Anonim Sirketi A cooling device and a control method
US9038404B2 (en) * 2011-04-19 2015-05-26 Liebert Corporation High efficiency cooling system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797560A (en) * 1972-06-21 1974-03-19 I Zaharoni Control system for environmental conditioning units
US3775995A (en) * 1972-07-17 1973-12-04 Westinghouse Electric Corp Variable capacity multiple compressor refrigeration system
GB2039386B (en) * 1979-01-05 1983-04-27 Lush L Control for refrigeration compressors
JPS5744788A (en) * 1980-08-30 1982-03-13 Toyoda Autom Loom Works Ltd Operation control method of compressor for vehicular air conditioner and its device
DE3210884A1 (de) * 1981-03-27 1982-10-14 Nippondenso Co., Ltd., Kariya, Aichi Kuehlsystem
US4480443A (en) * 1981-04-30 1984-11-06 Nippondenso Co., Ltd. Automotive refrigeration system

Also Published As

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DE3375842D1 (en) 1988-04-07
EP0118573A1 (de) 1984-09-19
AU1201883A (en) 1984-09-06
AU561404B2 (en) 1987-05-07

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